Pushbutton operated can opener

ABSTRACT

AN ELECTRICALLY POWERED CAN OPENER IS AUTOMATICALLY OPERATED BY SELECTIVELY DEPRESSING APPROPRIATE FINGER OPERATED PUSHBUTTONS. THE FIRST EMBODIMENT UTILIZES THE TOGGLING EFFECT OF A PIVOTAL PAWL AND ORBITING FEED WHEEL DRIVE SHAFT PINS TO OPEN OR CLOSE THE DISTANCE BETWEEN THE CAN FEED WHEEL AND THE CUTTER ELEMENT. THE SECOND EMBODIMENT INCLUDES A SPRING LOADED PAWL LEG THAT CUSHIONS TO ADVANCE OF THE CAN FEED WHEEL THROUGH THE CAN PIERCING ZONE WITH A MINIMUM OF TORQUE REQUIRED BY THE ELECTRIC MOTOR DRIVING SAME.

R. E. M LEAN PUSHBUTTON OPERATED CAN OPENER Oct. 12,1911

4 Sheets-Sheet 2 Filed Feb. 6, 1969 Ti?42 7751i INVENTOR Babe/#5. M04 @017 M Tror vg Oct. 12, 1971 R. E. M LEAN 3,611,565

PUSHBUTTON OPERATED CAN OPENER v Filed Feb. 6, 1969 4 Sheets-Sheet 3 INVENTOR Roby/*7 5. M61 0 Oct. 12, 197

E; MCLEAN 3,611,565

PUSHBUTTON OPERATED CAN OPENER Filed Feb. 6, 1969 4 Shams-Sheet i INVENTOR Rofierf 1f. McLean United States Paten 3,611,565 PUSHEUTTON OPERATED CAN OPENER Robert E. McLean, lRaytown, Mo., assignor to lRival Manufacturing Company Filed Feb. 6, 1969, Ser. No. 797,217 llnt. Cl. 1367b 7/38 US. Cl. 30-4 18 Claims ABSTRACT 015 THE DISCLOSURE An electrically powered can opener is automatically operated by selectively depressing appropriate finger operated pushbuttons. The first embodiment utilizes the toggling effect of a pivotal pawl and orbiting feed wheel drive shaft pins to open or close the distance between the can feed wheel and the cutter element. The second embodiment includes a spring loaded pawl leg that cushions the advance of the can feed wheel through the can piercing zone with a minimum of torque required by the electric motor driving same.

BRIEF DESCRIPTION OF THE INVENTION The can opener, described in more detail hereinafter, is one that requires no effort on the part of the user beyond the manually depressing of conventional finger-op erated pushbuttons.

The main operating elements of the can opener are affixed to or pivoted relative to the front frame of the can opener in accordance with the conventional procedure. The cutting element is affixed forwardly of the frame with a rotatable feed wheel which is movable between a position that would allow the inserting of the can in the can opener for opening purposes (or removal of the can) and a closed-up position which permits the end of the can to be sheared therefrom. This feed wheel (and its rotatable drive shaft) is carried by a yoke member between the two above-mentioned positions. The rearward portion of the feed wheel drive shaft has orbiting pins thereon which cooperate with two legs of a pushbutton controlled pivotal- 1y mounted pawl. The pawl is so oriented with respect to the orbiting pins that when in a first position one of the legs of the pawl and one of the orbiting pins form a toggle which will move the feed wheel drive shaft and feed wheel up into the can shearing position. The other leg of the pawl (likewise positionably controllable by the pushbuttons) may be alternately moved into the path of the orbiting pins so that a second toggle may be contracted. The contracting of same moves the feed wheel away from the cutting element so that the can may be either inserted in the can opener or removed therefrom.

A second embodiment of the invention includes the spring loading of one of the legs of the pawl so that the feed wheel drive shaft, as it is moved to the can shearing position, is cushioned by a compression spring, thereby effecting a power pierce condition as the can feed Wheel is advanced through the can piercing zone..This structure includes the locating of a compression spring within a suitable housing mounted on the appropriate leg of the pawl with the pin contacting a portion thereof positionable within the orbital path of the pins which rotate with the feed wheel drive shaft. When the spring loaded pawl leg is appropriately positioned for movement of the feed wheel up to a can shearing position, one of the orbiting pins contacts the spring loaded pawl leg and the movement of the shaft is thereby cushioned, since the spring load eventually results in the piercing of the end of the can as the can is being rotatively propelled by the feed wheel.

Both of the embodiments include a means for automatically de-energizing the electric motor once the end 3,fill,565 Patented Oct. l2, 1971i ice of the can has been sheared therefrom and both embodiments are constructed to prevent the jamming of the operating mechanism due to the structural orientation of the various interrelated parts.

One of the primary objects of the invention is to provide a power-operated can opener which may be entirely operated through a complete can opening cycle by merely depressing a conventional finger-operated pushbutton. It is an important feature of the first object that all phases of the cycle of events incident to the opening of a can and the release of same from the can opener after it has been opened, will automatically take place in response to the depressing of suitable pushbuttons.

Another object of the invention is to provide a can opener of the character described that requires only the momentary depressing of an appropriate pushbutton for the cycle of events incident to the opening of the can to be completed. Accordingly, it is: not necessary for the user to continue holding down the starting pushbutton after the end of the engaged can has been pierced by the cutting element.

Another object of the invention is to provide a can opener of the character described which includes a unique means for automatically de-energizing the power source as soon as the end of the can has been completely sheared from same. This unique means does not, however, prevent the continued holding of the can by the can opener until such time that the user would elect to remove the can therefrom.

A still further object of the invention is to provide a pushbutton operated can opener which has a uniquely constructed, inexpensive and reliable means for effecting the piercing of the end of the can by the cutting element as the can feed wheel is forced into a can end shearing position. It is a feature of this invention that the above mentioned uniquely constructed means is completely and reliably controlled by a pushbutton and that the can feed wheel will remain in the can shearing position until the end has been completely sheared from the can.

A still further object of the invention is to provide, in a can opener of the character described immediately above, a means for the retraction of the can feed wheel from the can shearing position and for the subsequent release of the can from the can opener without reversing the direction of the motor associated therewith, the can feed wheel, or the intermediate gearing. This retraction of the can feed wheel is accomplished by utilization of the abovementioned pushbuttons (or, alternately. the use of a single two-way push-button) and requires no effort other than the manual depressing of same.

Another object of the invention is to provide a pushbutton operated can opener which may be solely and entirelv operated by the manipulation of a pushbutton (or pushbuttons) mounted exteriorly of the can opener frame and which is of such a character that damage. either permanent or otherwise, is precluded if the pushbutton (or pushbuttons) is depressed longer than necessary to effect either the opening or the release of the can from the can opener.

A still further object of the invention is to provide in a can opener of the character described above. a uniquely constructed and reliable can feed wheel shifting means that will not be jammed or caused to malfunction if the user should inadvertently depress the pushbutton (or any one of the pushbuttons) at the wrong time or before the necessary time for one particular cycle to complete itself has lapsed.

Another and highly important object of the invention is to provide an electrically powered can opener whose operation is completely controlled by manipulating conventional push-buttons and wherein said can opener includes a means for causing the end of the can to begin to be sheared therefrom by the power pierce effect. One of the important features of this object is that the can feed wheel engages the underside of the rim of the can when the end of the can comes into firm contact with the periphery of the cutter wheel, however, the can feed wheel is cushioned by a spring load which enables the electric motor to gradually build up required torque before the spring pressure overcomes the resistance of the top of the can to pierce.

Another object of the invention is to provide an electrically operated can opener of the character described immediately above which includes a pivotal pawl positionable, in part, by the manipulation of the can opener pushbuttons and which has a compression spring integrally associated with one leg thereof. This construction allows the compression spring to form a toggle with the can feed wheel drive shaft orbiting pin so that movement of the drive shaft is cushioned by the spring load, thereby enabling the advancing of the can feed wheel through the can piercing zone to be accomplished with minimum torque requirement for the electric motor.

A further object of the invention is to provide in an electrical can opener of the character described above, a uniquely constructed means that permits the above-men tioned toggle to be completely extended and the cooperating pin to escape from the spring loaded pawl, thereby effectively preventing jamming of the mechanism in the event that the can should fail to be pierced by the cutter wheel. It is therefore a particularly important feature of the invention that the operating mechanism associated therewith will not jam, thereby allowing the can opening process to be repeated until completed.

A still further object of the invention is to provide in a can opener of the character described above a means for counterbalancing the pivotal movement of the abovementioned pawl so that a minimal amount of effort is required by the user in depressing the associated pushbuttons.

Other and further objects of the invention together with the features of novelty appurtenant thereto, will appear in the course of the following description.

DETAILED DESCRIPTION In the accompanying drawings, which form a part of the specification, and are to be read in conjunction therewith, and in which like reference numerals indicate like parts in the various views;

FIG. 1 is a fragmentary front elevational view of the upper portion of the can opener embodying my invention with the feed wheel shown in solid lines to indicate the raiser or can engaged position and in broken lines to show the lower or can releasing (and/or receiving) position;

FIG. 2 is a top plan view of the can opener shown in FIG. 1 but rotated 180 therefrom;

FIG. 3 is a rear elevational view of the can opener showing the various related parts in position to retract the can feed wheel away from the cutting element;

FIG. 4 is a sectional view taken along the line 44 of FIG. 2 in the direction of the arrows and showing most of the upper rear portion of the can opener frame and related parts;

FIG. 5 is a side elevational view of the can opener taken from the left-hand side of FIG. 3, with the parts to the left of the frame not shown;

FIG. 6 is a fragmentary sectional view taken generally along the line -66 of FIG. 3 in the direction of the arrows;

FIG. 7 is a rear view of the can opener showing the various parts of the second embodiment (spring loaded pawl) in elevation;

FIG. 8 is an elevational view of the spring loaded pawl, shown removed from the can opener frame, with a portion of the spring housing broken away to show the construction thereof; and

FIG. 9 is a sectional view taken generally along the line 9-9 of FIG. 8 in the direction of the arrows.

Referring now to the drawings, reference numeral 10 generally designates a body or upright frame of an electrically operated can opener. This frame may be fabricated in any desired manner and functionally operates to support most of the parts of the can opener. In commercial practice the frame cooperates with an open front box-like casing (not shown). The casing or housing may be of any suitable design or contour and, inasmuch as it forms no part of the present invention, it is not considered necessary to the understanding thereof.

Cutter wheel 11 (see FIG. 1) is located near the upper portion of frame 10 on an angled boss 12 which has been struck from frame 10. A stud or arbor 13 is anchored in boss 12 by hot-heading process and has a flanged portion 14 abutting same (FIG. 6). The conventional floating cutter wheel 11 is carried for free rotation and for possible limited wobble movement, when required, on the forward end of arbor 13. The combination screw and washer 15 maintain cutter wheel on the arbor, there being a compression coil spring 16 telescoped over arbor 13 between the arbor flange 14 and cutter wheel 11, biasing the wheel to the position shown in FIG. 6.

It should be understood that this arrangement relates to a mounting and structural configuration of a floating type cutter wheel, however, it should be stressed that nonfloating or simple blade type cutter element could be employed if desired.

Frame 10 further includes the mounting and locating of a fixed can guide 17, on its upper portion and which is also anchored therein by hot-heading process. The rim or flange of an engaged can will bear upwardly against same in a conventional manner. A spring can guide 18 is located to the left of cutter wheel 11 (as seen in FIG. 1) and has a flanged or paralleling portion 18a which is secured to frame 10 by rivet 19. Another rivet or frame extrusion 19a is interconnected with the paralleling portion 18a of the spring can guide and prevents same from inadvertent rotation due to the upward force thereon. The free end of the spring can guide 18 exerts a force or pressure downwardly on the rim or flange of a can when same is engaged in the can opener. In this manner, the rim or flange of the engaged can is forced downwardly on a toothed or serrated can feed wheel 20 so as to provide the necessary penetration of the teeth into the under edge of the can rim or flange, thereby assuring adequate traction for propelling or moving the can with respect to cut ter wheel 11.

A can guard 21 maintains an engaged can with its side wall at the desired angularity with respect to the end extremity of can feed wheel 20. This guard (21) is secured to frame 10 by rivet 22. An adequately spaced extrusion 23 cooperates with a mating hole in frame 10 to prevent unwanted rotation of the guard.

The above-mentioned feed wheel 20 is carried on a drive shaft (which will be discussed later) and is movably positionable by a yoke generally designated by the numeral 24. The yoke is pivoted on frame 10 for relatively free, but limited swinging by the attachment of leg 24a thereto. The other leg of yoke 24 (identified by the nu meral 24b) parallels leg 24a, the two legs being interconnected by the intermediate yoke portion 240.

For mounting purposes, leg 24a has a hardened flanged bushing 25 pressed therein. A three diameter (see FIG. 6) journal 26 is fitted interiorly of flanged bushing 25 at the intermediate diameter portion thereof. Spacer washer 27 is interposed between the rearward surface of frame 10 and the shoulder of the intermediate portion of journal 26 thereby facilitating in a proper spatial distance for the securing of journal 26 to frame 10 by rivet 22. When assembled, bushing 25 is free to rotate (thusly carrying leg 24:: of yoke 24) on journal 26, however, only a minimal amount of longitudinal movement of bushing 25 is permitted due to the presence of the largest diameter portion of journal 26 and washer 27.

A supporting bracket 28 is secured to frame 10 in a suitable manner (shown in FIG. 3 as being secured by screws 28a), and has its rearward end thereof extending parallel to rearward yoke leg 2412. A hardened shoulder stud 29 is hot-headed into the paralleled free end of bracket 28 with its forward end allowed to freely rotate within bushing 30 which has been pressed into the opposed portion, yoke leg 24b. In the assembled form, stud 29 is coaxial with rivet 22 and journal 26. It should be noted that yoke 24 is axially mounted on small hardened bearings for the purpose of minimizing friction when the yoke is being swung during operation of the can opener. Such a mounting permits the use of a minimal amount of motive power and also improves the efficiency and reliability of the automatic shutoff mechanism which will be discussed later in more detail.

As will be seen, the inherent minor torque and friction that tends to cause yoke 24 to be swung clockwise (FIG. 3) when the can is not engaged in the can opener and motor M is rotating, is stabilized by a curved spring washer 29:21. This washer is interposed between yoke leg 24b and bracket 28. Of course, other suitable friction-inducing means which provide the required resistance to the swinging of yoke 24 could be used, however, it should be noted that this resistance is slight and in no way in terferes with the intended later described swinging of yoke 24.

As suggested above, yoke 24 provides a means for carrying or supporting can feed wheel 20. To facilitate same, a three diameter feed wheel drive shaft bearing 31 is pressed into a suitable opening in leg 24a and through a collar 32 until the largest diameter portion of bearing 31 seats against leg 24a. A feed wheel drive shaft 33 is mounted for rotation in bearing 31 and extends through the rearward end thereof. The forward end (reduce diameter) portion of shaft 33 is threadably engaged within the journal portion (identified by numeral 201;) of can feed wheel 20 which is likewise located interiorly of the bearing. The rearward end of feed wheel drive shaft 33 is also reduced in diameter and has a disc or link 34 secured thereto by, preferably, hot-heading process. A conventional gear 35 is also hot-headed onto the rearward end of the drive shaft and same has a shoulder stud 36 secured thereto and extending forwardly therefrom so that the larger diameter portion of stud 36 is engaged in a slotted end of disc 34. Diametrically opposite stud 36 is another hardened shoulder stud 37 which is also anchored in disc 34 by hot-heading process but which extends forwardly of the disc (34). An arched leaf spring 38 is interposed between disc 34 and the rear end extremity of bearing 31, thereby urging can feed wheel 20 inwardly toward the bearing (31).

As may be clearly seen in FIGS. 1 and 6, can feed wheel 20 is supported exteriorly of frame 10. To facilitate same, the largest diameter portion of bearing 31 extends through an arcuate clearance slot 39 substantially located below cutter wheel 11 in frame 10. In this manner, the clockwise or counterclockwise rotation or swinging of yoke 24 (as seen in FIG. 4) is permitted, however, limited by bearing 31 contacting either of the extreme ends of the slot. It should be noted that, with the above structural design and orientation of yoke 24 and supporting bracket 28, the feed wheel drive shaft (33) may be assembled at any convenient time after the above-mentioned eelments have been located relative to frame 10.

The motive power for the can opener is supplied by electric motor M which, for economy reasons, may be of the shaded pole variety and supported relative to frame 10 by any suitable bracket means such as that shown in FIG. and indicated by the numeral 40. As is conventional, motor M has rotor shaft 41 extending outwardly therefrom with a helical pinion gear 42 integral with the intermediate portion of the forward shaft section between a suitable bearing (not shown) and the motor itself. The rearward portion of the shaft 41 extends through a hearing at the rear of motor M and may be further extended 6 and used for mounting a cutlery grinding wheel thereon if desired.

The reduction gears, which are associated with the above-mentioned pinion gear 42 and which will be discussed in more detail, are in part supported on bracket 43 which is connected to and off set rearwardly but parallel to frame 10. As seen in FIG. 6, the parallel portion of bracket 43 has shoulder studs 44 and 45 anchored therein (preferably by hot-heading process) and extending rearwardly therefrom. Stud 44 has gear 46a and pinion 46b mounted thereon for free rotation so that gear 46a engages pinion 42. Stud 45 is coaxial with rivet 22, journal 26 and yoke mounting stud 29 and has another gear 47a and pinion 47b mounted for rotation thereon. The teeth of pinion 47b mesh with teeth of gear 35 which, as was mentioned above, has been hot-headed onto the rearward end of drive shaft 33. It should be noted at this point that the distance between axis of stud 45 and the axis of can feed drive shaft 33 is also the center distance between pinion 47b and gear 35 and that this distance is not altered as yoke 24 swings within the limits of arcuate slot 39 from one extreme position to the other. The abovedescribed gear train provides a three-stage reduction between motor shaft 41 and can feed wheel 20. Also the cooperating portions of the yoke and the various supporting brackets provide for a convenient assembly and limit the axial movement of the various gears and pinions so that they are not moved beyond desired axial limits.

As suggested above, the swinging of yoke 24 carries can feed wheel 20 for movement between the broken line and the solid line positions shown in FIG. 1. It is necessary to swing yoke 24 to its extreme counterclockwise position (as seen in broken line position of FIG. 4) in order to lower can feed wheel 20 to the broken line position shown in FIG. 1 so that a can may be inserted in the can opener for the opening thereof. The swinging of yoke 24 to this position is also required for releasing an opened can from the can opener. Conversely, it is necessary to swing yoke 24 to its extreme clockwise position (shown by the solid lines in FIG. 4 in its approximate position) to raise can feed wheel 20 to the solid line position shown in FIG. 1. Movement of same to the solid line position is required to effect the piercing of the end of the can by cutter wheel 11 and to bring can feed wheel '20 into proper can end shearing relationship with the cutter wheel. When can feed wheel 20 is in its uppermost position (see solid line of FIG. 1) and has a can engaged thereon, resistance of the end of the can to shear by cutter wheel 11 causes a resultant force that tends to swing yoke 24 in a clockwise direction (as viewed in FIGS. 3 and 4). I have found that such a force allows the yoke to remain in the extreme position even when the axis of can feed wheel 20 is stopped as much as 10 degrees ahead of vertical line extending through the axis on which yoke 24 is swingably mounted. Accordingly, the required vertical displacement of can feed wheel 21} can be accomplished with fewer degrees of swinging movement of yoke 24 than would be required for a like amount of vertical movement if the axis of feed wheel 20 were permitted to move into the vertical plane mentioned above.

As suggested above, a means is provided for initiating and positively causing the swinging movement of yoke 24. An integral portion of this means is pawl 48 (see FIGS. 3 and 4) which is pivotally mounted on a stud 49 that is anchored in frame 10. The pawl has an upper leg 48 a and a lower leg 48!), each leg having contoured or shaped end extremities for cooperation with the pin 37 as will be explained in more detail later. For example, upper leg 48a has a notch 48a located therein and which is movable into the orbit of pin 37. Likewise, the lower leg 48b contains a notch 48b which is formed by the upward extension of a finger projection at the end extremity of the leg.

Pawl 48 has a stud 5t] anchored in the heel thereof. This stud provides a pivotal mounting for one end of link 51 and thereby means to effect the swinging of the pawl about stud 49 as will be described later. The end of link 51 opposite stud 50 contains an elliptical slot 51a (see FIG. 4) through which the stud 53 is allowed to freely extend, same being fixedly anchored in frame 10. As seen in FIGS. 3 and 4, the left end of link 51 has a rearwardly turned lug portion 5111 (see FIG. 5 with opposed notches on the end portion thereof. A coil spring 52. is hooked over the notches in lug 51b while the other end (see FIGS. 2, 3, and 4) is located within groove 49a in stud 49'. It should be understood that link 51 and the heel portion of pawl 48 form a toggle and that spring 52 urges pawl 48 to rotate in a clockwise direction (as viewed in FIGS. '3 and 4) on its pivot stud 49 toward stop stud 53a whenever the axis of stud 50 is above a straight line that would extend through the axes of studs 49' and 53. In a similar manner, whenever the axis of stud 50 is below the abovementioned imaginary straight line between studs 49 and '53, then the action of spring 52 will urge pawl 48 to rotate counterclockwise (FIGS. 3 and 4) on pivot stud 49 toward the upper stop stud 54. Of course, both stop studs 53a and 54 are anchored to frame and extend rearwardly therefrom.

The legs 48:: and 48b of pawl 48 are so spaced with respect to one another that only one of the legs can be in the orbital path of pin 37 at any given time. Accordingly, the mechanism will not be jammed by the simultaneous engagement of both legs with pin 37. It should be noted that an earlier average engagement of pin 37 with either of the pawl notches 48a or 481) may be accomplished by mounting a second pin or stud diametrically across the axis of the can feed wheel drive shaft 33 from the illustrated position ofstud 37.

In order to exercise switch control (to energize electric motor M) and to help initiate the swinging of pawl 48, a plate 55 is pivotally mounted on stud 53 (mentioned above as also pivotally mounting link 51). A tension coil spring 56 is connected through an opening in the lower portion of plate 55 while its other end is hooked in a groove in stud 57 which is anchored in frame 10 and extends rearwardly thereof. This spring normally biases plate 55 to the position shown in FIG. 4.

The swinging movement of plate 55 is initiated by the two pushbuttons and their associated control rods which will now be discussed. A first control rod 58 is located so that its lower forwardly turned end is pivotally connected within an opening in plate 55 to the left of pivot stud 53. The upper end of control rod 58 is pressed into pushbutton 58a which extends, for reciprocating movement, through a suitable opening in a bracket 59 that has been secured to frame 10 by any convenient means. A second control rod 60 also has its lower forwardly angled end pivotally extending through a suitable opening of plate 55 located to the right of pivot stud 53 and with its (rod 60) upper end pressed into pushbutton 6011 which extends through another suitable opening in bracket 59. It should be pointed out that both control rods are pivoted to plate 55 at the same vertical elevation, thereby making plate 55 pivotally responsive to equal amounts of pressure on either pushbutton. As seen in FIG. 3, stop studs 60b and 600 are anchored to frame 10 extending rearwardly therefrom for the purpose of limiting the counterclockwise and clockwise respective swinging movement of plate 55. It should be understood that in lieu of separate individual pushbuttons 58a and 60a, a conventional single rockable type push-buton could be interconnected with plate 55 by one of the control rods for initiating the swinging movement of plate 55, in accordance with the application of force on a selective side of the single push-button.

Located between plate 55 and frame 10 are two pivotally mounted links 61 and 62 which have rearwardly turned end portions 61a and 62a, respectively. Link 61 is mounted on shoulder stud 61b (anchored in plate 55) while link 62 is mounted on shoulder stud 62b (also anchored in plate 55) each mounting allowing the pivotal movement of its respective link. As seen in FIGS. 3 and 4, the rearwardly turned portions (61a and 62a) of the two links are precluded from any further movement towards each other due to the fact that the end portions 61A and 62A respectively contact the upper and lower notched portions of plate 55 (these notched portions being identified by the numerals 55a and 55b, respectively). A coil spring 63 of suitable tension has its upper end hooked over rearward extension 61a and its lower end hooked over a suitable notch in extension 62a. As a result, this spring urges links 61 and 62 toward each other until the rearward extensions of same seat in notches 55a and 55b, respectively, and are thereby straddling link 51.

A flanged bracket B is afiixed to frame 10 below plate 55 by any suitable means such as by the screws shown in FIGS. 3 and 4. A conventional switch S of the over-center design (having a spring means that normally biases its contacts open) is aflixed to bracket B in the usual manner.

An actuating rod, generally designated by the numeral 64, has a short lower horizontal portion 64a which extends through a suitable aperture in the rearwardly turned portion of bracket B and engages the insulated lever L of switch S. The actuating rod then extends vertically 64b) from the horizontal portion 64a to a longer upper horizontal portion 640 and is then terminated in a hooked or looped portion 64d. A slotted bracket, 65, (see FIG. 5) is secured to frame 10 by any convenient means (such as the screws shown in FIGS. 3 and 4) and operates to confine and guide the upper horizontal portion 640 of actuating rod 64 as it moves therewithin.

As suggested above, a means is provided to automatically shut off motor M once the end of the can has been completely severed. This automatic shut off means includes a bell crank 66 (see FIGS. 3 and 4) which is pivotally mounted relative to frame 10 on shoulder rivet 67. The bell crank has a substantially horizontal leg 66a and a substantially vertical leg 66b, with the crank itself being pivotally connected on rivet 67 at the heel thereof. A stop stud 67a extends from frame 10 which is appropriately located to limit the clockwise rotation of the bell crank when viewed in the figures immediately mentioned above.

The clockwise rotation of the bell crank is urged by the location of a suitable coil spring 68 which is connected at its lower end to a frame stud 69 and at its upper end to horizontal leg 66a of bell crank 66 (FIGS. 3 and 4), either directly or via an adjustable bolt and flange combination generally shown by the numeral 70.

A shoulder stud 71 has its head portion positioned between frame 10 and bell crank 66 so that it extends rearwardly through the free end of leg 66b and through a flanged collar 72. The hook portion 64d of the actuating rod 64 is positioned over the smaller diameter portion of flanged collar 72 and is free to slide to the right thereon at any time (when viewed in FIGS. 3 and 4). The head portion of shoulder stud 71 is engageable by the vertically extending lug (identified by the numeral 24a) which is an integral portion of leg 24a of the yoke 24.

The physical orientation of actuating rod 64 is such that the action of the spring means of switch S will urge horizontal portion 64a (and the remainder of the actuating rod) to the left as seen in FIGS. 3 and 4. This urging or spring biasing may be supplemented by another spring if desired. It is also of interest to note that the vertical portion 64b of actuating rod 64 is engageable by either of the rearwardly turned portions 61a or 62a of the pivotal links 61 and 62, respectively.

OPERATION OF THE FIRST EMBODIMENT Turning now to the operation of the first embodiment which has been disclosed in FIGS. 1-6, if can feed wheel 20 is not in its lower or can receiving position as indicated by the broken lines in FIG. 1, the user first depresses the can release pushbutton 60a and maintains it in this depressed condition until can feed wheel 20 moves to the desired position. The normal cycle of opening of any can would, however, have left the can feed wheel in this position from the prior operation thereof.

The user inserts the can to be opened in the can opener by holding its upper end in engagement with the cutting periphery of over-lying cutter wheel 11 and then fully depresses the starting push-button 58a and holds same in a depressed condition until the end of the can has been fully pierced by cutter wheel 11. It is not necessary for the user to hold start pushbutton 58a depressed after the end of the can has been fully pierced by cutter wheel 11 and, in fact, the can opener needs no further attention until the user desires to release the opened can from the can opener.

Prior to the user depressing starting pushbutton 58a, the pawl 48 Was in the position shown in FIG. 3, with the upper leg 48a seated counterclockwise against stop stud 54 and with yoke 24 having carried can feed wheel to the broken line position shown in FIG. 4. When starting pushbutton 58a is fully depressed, plate 55 is swung on its pivot stud 53 to its full counterclockwise position, i.e. its upper left edge contacting stop stud 6011. With plate 55 in this position, link portion 62a engages the vertical portion 64b of actuating rod 64 and moves same to the right when viewed in FIG. 4. This actuating rod condition causes the horizontal portion of same (64a) to move insulating lever L in such a manner to initiate the closing of the contact points of switch S. The closing of the contacts of switch S connects motor M to a suitable source of electrical power and will cause same to begin to rotate. While this was occurring, the hooked end 64d of actuating rod 64 has been allowed to freely slide on flanged collar 72.

While actuating rod 64 was being moved as described above, the upper edge of link portion 62a comes in contact with and engages the lower edge portion of link 51 intermediate the axes of studs and 53. Assuming the orbiting pin 37 was not in a position to interfere with the swinging movement of pawl 48, same will be moved to the solid line position shown in FIG. 4. If it results that pin 37 would interfere with swinging of pawl 48 to its seated position against stop stud 53a, the rearwardly turned link portion 62a will unseat from notch b (of plate 55) against the tension of spring 63. As soon as pin 37 has orbited slightly about the axis of can feed wheel drive shaft 33, the action of spring 63 moves link portion 62a to its seat within the notch 55b. This action concurrently results in the swinging (clockwise) of pawl 48 to be fully seated against stop stud 53a (the above seating taking place in not over one revolution of can feed wheel drive shaft 33). Orbiting pin 37 will then be engaged within notch 48a, of upper leg 484 so that additional counterclockwise rotation (see in FIGS. 3 and 4) of the feed wheel drive shaft 33 results in the movement of drive shaft 33 from its lowermost position to the upper or solid line position shown in FIG. 4. As feed wheel drive shaft 33 is being moved upwardly and to the right, pin 37 is pivoted within notch 48a. This movement is actually the result of the straightening out of a toggle which would be comprised of upper leg 48a of pawl 48 acting as one leg of the toggle while the link 34 carrying the pm 37 acts as a second leg thereof. Accordingly, drive shaft 33 and wheel 20 are moved upwardly in a can piercing direction as the toggle is straightened.

Immediately thereafter, pin 37 is free to escape from notch 48a of pawl 48 and is allowed to ratchet thereafter as drive shaft 33 continues to rotate in its counterclockwise direction (FIG. 4).

In the embodiment discussed immediately above, can feed wheel drive shaft 33 actually moves slightly farther to the right (FIG. 4) after the toggle has been fully straightened. This is accomplished by the inherent force resulting from the traction of the teeth of can feed wheel 20 against the under edge of the flange of the engaged can end and to the resistance of the can top as it is being sheared by cutter wheel 11. In actual practice, feed wheel drive shaft 33 moves as much as of an inch to the right of the position illustrated by the solid line pawl position shown in FIG. 4. It should be noted that this additional movement causes the pin 37 to actually clear the leg 48a of pawl 48 while the end is being sheared from the can. This additional movement also results in the engagement of the lug portion 24a of yoke leg 24a with the head of the shoulder stud 71. As stud 71 is anchored in the free end of vertical leg 66b of bell crank 66, the resultant movement (caused by the engagement of lug 24a therewith) is the counterclockwise swinging of bell crank 66 on its pivot stud 67 until leg 66a is substantially horizontal. With leg 66a in this position, tension spring 68 is further elongated, thereby increasing the bias on bell crank 66 and causing it to swing clockwise on pivot stud 67 (FIG. 4) after the end of an engaged can has been completely sheared. I have found that as long as the end is being sheared from the can, the combined forces urging can feed wheel drive shaft 33 to the right (FIGS. 3 and 4) always overcome the tension of spring 68 so that the position of bell crank 66 maintains actuating rod 64 in its rightmost position, thereby keeping the switch S contacts closed and the motor M in an energized state.

Under normal conditions and absent a can to be opened, the withdrawing of manual force from either of the two pushbuttons allows spring 56 to immediately return plate 55 to the position shown in FIG. 4, thereby disengaging either link 61 or link 62 from the actuating rod vertical section 64b so that spring action in switch S returns rod 64 to the left (FIGS. 3 and 4) and allows the switch contacts to open and the motor to shut off. Likewise, as soon as the end has been completely sheared from the can, the tension of spring 68 overcomes the combined forces that urge the feed wheel drive shaft 33 to the right (FIG. 4) and bell crank 66 is swung clockwise on its pivot stud until the free end 66a seats against stop stud 67a. This swinging automatically shuts off the motor M as switch actuating rod 64 is spring returned to the position allowing separation of the contacts of switch S.

The release of the can from the can opener is obtained merely by depressing the release pushbutton 60a and maintaining same in its fully depressed condition until can feed wheel 20 arrives at the position shown in the broken lines in FIG. 1. Prior to release pushbutton 6011 being depressed, pawl 48 is in the solid line position shown in FIG. 4, with the lower leg 48.) seated against stop stud 53a and with feed wheel drive shaft 33 substantially in the position shown in FIG. 4. The downward movement of release push-button 60a exerts a clockwise force on plate 55 via control rod 60 until the plates lower left hand portion (FIG. 4) contacts stop stud 600. This movement also results in the engagement of link portion 61a with the vertical portion 64b of switch actuating rod 64 and the movement of rod 64 to the right, thereby closing of the switch S contacts and energizing motor M. This action is similar to the counterclockwise swinging of plate 55, in that the lower edge of link portion 61a contacts the upper edge of link 51 intermediate the axes of studs 50 and 53 and, absent interference of pin 37, pawl 48 is moved to the position shown in FIG. 3, with upper leg 48a seating against stop stud 54. Assuming pin 37 was in a position to interfere with the swinging of pawl 48 to its counterclockwise position, link portion'61a would unseat from notch 55a of plate 55 against the urging of spring 63. However, as soon as pin 37 has orbited slightly around the axis of feed wheel shaft 33, the action of spring 63 would move link portion 61a into notch 55a, concurrently swinging pawl 48 into full engagement with stop stud 54.

The seating of pawl 48 to the broken line position shown in FIG. 4 will occur in not over one revolution of feed wheel shaft 33, whereupon the orbiting pin 37 will eventually engage notch 48b in the lower pawl leg 48b so that additional counterclockwise rotation of shaft 33 moves same from its uppermost position to its lowermost position. Note that during the above-mentioned movement, pin 37 pivoted in notch 48b in pawl leg 48b and that this movement of drive shaft 33 resulted from the contracting of an overcenter toggle from its extended condition. After the toggle was contracted (note broken lines in FIG. 4) the pin 37 is free to escape from notch 48b and may rachet thereafter as the can feed wheel continues to rotate counterclockwise in any number of revolutions. Actually, feed wheel drive shaft 33 can be moved slightly further to the left (as seen in FIG. 4) after the toggle has been contracted, in order to prevent any harmful interference between pin 37 and pawl 48. Furthermore, the clockwise and counterclockwise swinging of yoke 24 is positively limited by the engagement of the largest diameter portion of bearing 31 with either end of arcuate slot 39.

By referring to the broken line positions of upper leg 48a of pawl 48 and bearing 31 (as seen in FIG. 4), as the pawl 48 is swung clockwise on pivot stud 49, the free end of upper leg 48a will first seat on bearing 31, thereby positioning the notch 48a as to best receive pin 37 to form the contracted toggle. This is, of course, required before the toggle can be extended.

As discussed above, the can guard 21 and the various can guides operate to assure optimum orientation of the can and can end relative to the feed wheel and cutter element. The yoke 24 has been mounted on the small hardened axial bearings in order to provide as nearly friction free swinging of same as is possible within realistic economic limits. This affords maximum advantage to the automatic shut off mechanism and permits the use of a smaller electrical motor from a power requirement standpoint. Likewise, the above arrangement of the floating cutter wheel 11 accommodates the thick side overlapping seam common in cans to be opened, thereby further aiding and insuring in the trouble free operation of the entire unit.

THE SPRING LOAD 'PAWL Turning now to a more detailed discussion of the second embodiment of my invention, FIGS. 79 generally illustrate the operative parts as they relate to the can opener operation discussed above. Inasmuch as all the parts forward of frame are the same as those discussed above with reference to FIGS. 1-6, they are not shown or discussed in any detail.

This embodiment includes a yoke 73 which is essentially the same as yoke 24 supra, except that the free end of the rearward leg 73a extends below the pivot stud 74 and has a stud 75 which extends rearwardly from the lower portion thereof. A spring 76 is hooked in a groove in the rearward end portion of stud 75 while the other end is hooked in a groove in stud 77 which is anchored in and extends rearwardly from bracket 78, (same corresponding in function to the supporting bracket 28 of the first embodiment).

Mounted on either side of feed wheel drive shaft 33 (affixed to a suitable link or disc similar to link or disc 34 in the first embodiment) are two hardened shoulder studs 78, hereinafter referred to as pins, which act as pawl engaging pins similar to pin 37 of the first embodiment. It should be understood that only one of the pins 78 is necessary for operating embodiment shown in FIG. 7, however, in order to provide, on the average, a faster acting can opening operation, two such pins may be utilized.

Pawl 79 is pivoted to frame 10 on pivot stud 80, which is anchored in frame 10, and is swingable between stop stud 81 and lower stop stud 82. A stud 83 is anchored in the main body of pawl 79 and has at least three circumferential grooves located in the rearwardly extending surface thereof. The tension spring 84 has its lower end hooked in the forwardmost groove of stud 83 (that being the groove nearest pawl 79) while the other end of this spring is hooked over the stud 85, anchored in frame 10, and located within a suitable groove therein.

A switch actuating plate 86 is pivoted for free rotation on stud 86a, however stop studs 87 and 88b extend from frame 10 and are operative to limit the clockwise and counterclockwise rotation respectively of the actuating plate. Spring 88 has its lower end hooked around the suitable groove in stud 88a, anchored in frame 10, with its upper end hooked through a suitable aperture in the lower right portion of plate 86, thereby biasing plate 86 to the position shown in FIG. 7. The upper end portion of plate 86 is provided with the turned over lugs 86b and 860, which are laterally spaced an equal distance from a vertical center line through the pivot axis of plate 86. A pair of tension springs 89 and 90 are hooked over lugs 86b and 860 respectively at their lower ends thereof and have their upper ends (which are bent into the shape of an elongated U) hooked over stud 83 within the two rearward grooves therein. In actual practice, the lugs (86b and 86c) are suitably staggered in parallel vertical planes, thereby facilitating the location of spring 89 and 90 in different spaced apart grooves in stud 83.

Switch S is mounted to frame 10 in a manner similar to that described above, however, with the insulated actuating lever located in a substantially horizontal plane. An actuating rod generally indicated by the numeral 91 has a vertical portion 91a which extends through suitable aperture in switch S supporting bracket, with its lower end extremity turned forwardly in a horizontal plane and in contact with the insulated lever of the switch. A substantially horizontal portion of switch actuating rod 91 (identified by the numeral 91b) is at a rest condition (see FIG. 7) upon the upper surface of lugs 86b and 860 of plate 86. The remainder of the switch actuating rod 91 extends upwardly and curves to the right where it eventually locates in a notch 92a. of the pivotally mounted bell crank 92. (Bell crank 92 is substantially similar to bell crank 66.)

Control rod 93 is pivotally located in the left side of plate 86 with same having its upper end pressed into start pushbutton 93a. The right hand control rod 94 is likewise pivotally interconnected with the right hand portion of plate 86 and also extends upwardly, terminating within the release pushbutton 94a. A highly important feature of the second embodiment is the spring loading of the upper pawl leg hereinafter identified by the numeral 79a. It is this leg that engages and/ or releases orbiting pins 78 and which functions in a somewhat similar manner as upper leg 48a (of the first embodiment) with the exception of What will now be described.

The detailed construction of spring loaded pawl leg 79a is best shown in FIGS. 8 and 9. As viewed therein, a pair of contoured (to accommodate a later described compression spring) side plates 96a and 96b are attached to the upper right hand portion of the main body of pawl 79*. The two plates are fastened to the upper right hand end portion of pawl 79 by the two rivets 97a and 971) which extend through suitable apertures in both plates and through an appropriate portion of the pawl itself.

The outer rivet 98 joins the right hand end of the plates 96a and 96b, however, an additional spacer member (not shown) may be located between the two opposed ears 98' which accommodate rivet 98, or a portion of plate 96b may be suitably offset. It may therefore be seen that the above-described plates comprise a portion of the housing for compression spring 99. This spring has its left hand end portion (FIG. 8) abutting the main body of pawl 79 while the opposite end thereof is located interiorly of a slot formed by the bifurcated left end portion of the pin contacting extension or slide 79a of the upper leg 79a. The pin contacting extension 79a is allowed to reciprocally move within the housing described above, however, the outward movement is limited by a lug 99 (which protrudes upwardly through a slot formed by the upper parallel portions of the plates 96a. and 9611) coming into contact with the spacer located between ears 98. The contracted travel of extension 79a will likewise be limited by the engagement of the left hand portion of lug 99 against the exterior face of the main body of pawl 79. Accordingly, the action of compression spring 99 is to urge extension 79a' outwardly, however, the extension can be moved inwardly when an exterior force overcomes the spring load. The advantages of this feature relative to the functioning of the opener will now be described, infra.

The second embodiment of my can opener is operated by the user in the same manner as that described above with reference to the first embodiment. In this regard, can feed wheel 20 is away from cutter wheel 11 (as shown by the broken line position of same in FIG. 1) after a can has been previously removed from the opener. With yoke 73 in the position shown in FIG. 7, the action of spring 76 will overcome any unwanted tendency of yoke 73 to rotate clockwise. 'It should be noted, however, that when the parts of the can opener are in the can end shearing position, the axes of pins 74, 75, and 77 will lie substantially in a straight line, thereby negating any action on the part of spring 76 to rotate yoke 73 in either direction.

Spring 84 maintains pawl 79 in either extreme clockwise or counterclockwise position (after being rotated thereto). Since pawl 79 is counterbalanced, the force or tension of spring 84 may be substantially reduced from that which would ordinarily be required to finally locate pawl 79 in either of the above-mentioned positions. This reduced spring tension results in less force being required on either pushbutton (93a or 94a) to swing the pawl from one position to another.

As may be clearly seen in FIG. 7, spring 84 is positioned to urge rotation of the pawl to either extreme location, the direction of rotation depending upon the position of stud 83 relative to pivot stud 80. The stud 83 is so positioned that it travels in an arcuate path relative to pivot stud 80 and will be at an equal disance from a vertical plane through the center of stud 80 when on either the extreme right or the extreme left side thereof. Of course, when spring 84 is either left or right of the vertical plane, it acts to urge pawl 79 either clockwise or counterclockwise respectively about pivot stud 80.

Spring 88 normally biases plate 86 to assume the intermediate position shown in FIG. 7, thusly maintaining the two pushbuttons 93a and 94a in the same horizontal plane. In this position, neither of the springs 89 or 90 is under any tension (both springs are identical in length) nor are they affected by swinging of pawl 79 in either direction. However, the tension in either of the springs 89 or 90 (when either of the pushbnttons is fully depressed) is adequate to overcome the action of spring 84, thereby resulting in the swinging of pawl 79 to the appropriate extreme position at any time that one of pins 78 does not prevent such pawl movement. Should the engagement of either of the orbiting pins 78 temporarily prevent the rotation of pawl 79 to either its extreme clockwise or counterclockwise position, then the action of either spring 89 or 90 will respectively rotate the pawl to the desired extreme position when the corresponding push-button (93a or 94a) is held fully depressed until the temporary pin interference no longer exists.

Motor M is conveniently energized by the depressing of either of the two push-buttons mentioned above. For example, when push-button 94a is depressed, plate 86 pivots in a clockwise direction which causes the upper surface of lug 86b to contact and lift control rod 91. This rod movement pulls up on the insulated lever of switch S and closes normally open contacts to energize the motor. Likewise, the depressing of push-button 93a rotates plate 86 in a counterclockwise direction, causing the upper surface of lug 86c to lift up on the horizontal section 9111 of rod 91, thereby similarly resulting in the closing of the normally open switch contacts. The above-mentioned upward movement of actuating rod 91 is facilitated at its upper end by the elongate slot 92a and bell crank 92 which allows the forwardly turned 141 portion of the actuating rod to move upwardly within notch 92a.

As was pointed out with reference to the embodiment disclosed in FIGS. 1-6, yoke 73 likewise has an upstanding lug 7312 which is oriented so that when swung in a clockwise direction about pivot stud 74, it will contact rearwardly extending stud 92b. As lug 73b moves against stud 92b (located on the lower vertical portion of bell crank), the bell crank 92 is rotated in a counterclockwise direction. This rotation is against the tension of spring 100, however, the bell crank will remain with leg 920 of same nearly horizontal while the end of the can is being sheared by cutter wheel 11. In this position, actuating rod 91 is lifted (or maintained in a lifted position), the switch contacts closed and motor M in an energized state. After the top has been sheared from the engaged can, the action of spring 100 will overcome the forces tending to rotate yoke 73 clockwise, enabling the substantially horizontal leg 92c to return to its rest position against stop stud 101 and allowing switch actuating rod 91 to return to its rest position on the upper surface of lugs 86]; and 860. This returned or rest position permits the contacts of switch S to open and the motor to be automatically shut off.

Turning now to a more detailed discussion of the advantages and operation of the spring loaded pawl extension 79a, it should be noted that it is the toggling of either one of orbiting pins 78 within the notch in the said upper pawl leg extension 79a that moves can feed wheel 20 from its broken line or open position shown in FIG. 1 to the solid line or can end shearing position also shown therein. Thus, it will be seen that when the can feed wheel is engaged solidly under the rim or flange of the can and the end of the can is firmly positioned under cutter wheel 11, the cushioning of spring 99, as the toggle straightens out toward its extended condition, enables the electric motor M to gradually build up required can piercing pressure in the pawl compression spring (99). As a result, the advancing of can feed wheel 20 through the can piercing zone may be accomplished with a minimum of torque from the electric motor. Although upward and lateral movement of the feed wheel (for piercing of the end of the can by the cutter wheel) is briefly delayed while the electric motor builds up additional pressure in spring 99, it is to be pointed out that the feed wheel 20 simultaneously advances the can, thus enabling piercing of the end of the can with less force than otherwise would be required. (This action is commonly known as power pierce) To review the sequence of the events that start the can opening process, assume that can feed wheel 20 is in the broken line position shown in FIG. 1 and that pawl 79 and yoke 73 are in the position shown in FIG. 7. The can is inserted for opening with the rim or flange located on the upper surface of can feed wheel 20. Start pushbutton 93a is depressed, swinging plate 86 in a counterclockwise direction against the tension of coil spring 88. As plate 36 swings about pivot stud 86a, lug 86b is moved downwardly, pulling the lower end of spring 89 therewith and exerting a downward force on stud 83 (around which spring 89 has been hooked). At the same time, pawl 79 is swung (due to the pulling force via spring 89) about its pivot axis 80 until same reaches its extreme clockwise position. When stud 83 moves past the vertical plane through the center of pivot axis 80, spring 84 assists in the movement of pawl 79 to this extreme position.

As described above, the pivoting of plate 86 has moved actuating rod 91 upwardly and has resulted in the closing of normally open contacts of switch S so that motor M is energized. If pawl leg extension 79a has not been interfered with by the presence of any one of the orbiting pins 78 it was therefore able to assume its extreme clockwise position (otherwise the pawl leg merely rides over the interfering pin until pawl 79 eventually assumes the extreme position mentioned above). One of the pins 78 eventually engages in the notch of upper leg extension 79a and begins the toggling action therewith. As the toggle moves to its extended position, can feed wheel moves the can upwardly against the cutter wheel 11, under the cushioning effect of compression spring 99. The continued rotation of can feed wheel 20 results in the power pierce effect which has been fully described in my Pat. No. 3,277,570 and in US. Pats. Nos. 2,902,757; 3,018,548; and 3,078,568.

Should the end of the engaged can for any reason fail to be pierced by cutter wheel 11, spring 99 and pawl extension 79a nevertheless allow the toggle to be completely straightened out so that orbiting pin 78 may escape from the notch. This prevents jamming of the mechanism and additionally frees same in order that the can feed wheel can be returned to its lower-most position by depressing the release pushbutton 94a. The opening process then may be repeated to effect the piercing and shearing of the end of the can.

For maximum piercing efficiency, compression spring 99 should be designed so that the pressure exerted in piercing the end of the can may be done with a minimum of required torque on feed wheel 20. However, the spring must be adequate to assure piercing of the end of conventional cans when properly presented and inserted within the can opener.

As suggested above, upper leg extension 79a is limited within its housing between a fully extended position (with lug 99' contacting the left hand portion of car 98) and a fully retracted position (with left hand portion of lug 99 engaging the end extremity of the main portion of pawl 79). This distance (the movable reciprocating distance of extension 79a) is sufficient so that the pins 78 may be released from the notch of extension 7 9a if perhaps the cutter wheel 11 failed to pierce the end of the engaged can. Accordingly, the orbiting pins will be allowed to leave the above-mentioned notch and to re-enter same, so that the power pierce process may again be repeated under the cushioning effect of compression spring 99.

It is to be pointed out that, in a can opener construction in which a single pin 37 or 78 is used (in conjunction with spring loading of the upper leg of pawl 48, FIG. 4, or the upper leg of pawl 79, FIG. 7), the stop stud 53a or stop stud 82 respectively, could be repositioned as necessary to permit some additional clockwise rotation of pawl 48 or pawl 79. In this manner, no pressure or force of the pawl compression spring 99 would be imparted to orbiting pin 37 or 78 at times when such pin would actually escape from notch of extension 79a. Accordingly, there would be no audible sound as either pin 37 or pin 78 would escape from the notch of extension 79a should the end of any can fail to be pierced by cutter Wheel 11.

The remainder of the can opener operates substantially similar to the above description with reference to the first embodiment in that can release and automatic shutoff of can opener motor M are effected in similar manner.

From the foregoing, it will be seen that this invention is one well adapted to attain all of the ends and objects hereinabove set forth together with other advantages which are obvious and which are inherent to the structure.

It will be understood that certain features and subcombinations are of utility and may be employed without reference to other features and subcombinations. This is contemplated by and is within the scope of the claims.

As many possible embodiments may be made of the invention without departing from the scope thereof, it is to be understood that all matter herein set forth or shown in the accompanying drawings is to be interpreted as illustrative and not in a limiting sense.

Having thus described my invention, I claim:

1. In a power operated can opener having an upright 16 frame, a can feed wheel, and a cutting element mounted on said frame, the improvement comprising:

a can feed wheel carrier member carrying a feed wheel shaft with said feed wheel located thereon, said carrier member pivoted to said frame and movable between positions that will permit a can to be received by said can opener and retained thereby for the purpose of cutting same, or to be selectively removed from the retaining position,

a pin member carried by and radially offset from said feed wheel shaft for orbital travel about said shaft,

a pawl member pivoted to said frame, said pawl member having a pin engaging portion,

a pushbutton,

means interconnecting said pushbutton and said pawl member, said pin member and said pawl member being selectively positionable in response to the actuation of said pushbutton so that said pawl member engages said pin member and forces said feed wheel carrier member and said feed wheel into a position that will retain a can in operative relationship with respect to said cutting element for cutting purposes, and

an electric motor drivingly connected with said feed wheel, said motor selectively energized in response to the actuation of said pushbutton and said movement of said feed wheel into said can cutting position.

2. The invention as in claim 1 wherein said pawl member and said pin member forms a toggle linkage that interconnects said carrier member and said frame, said linkage having a fully extended condition corresponding to said can cutting position and a retracted or folded condition corresponding to said can receiving (or can removing) position.

3. The invention as in claim 2 wherein said can opener includes a motor control means having a switch means which is operable, responsive to the upward movement of said feed wheel to energize said motor prior to piercing of the can end by said cutter element.

4. The invention as in claim 2 wherein said pawl has two spaced apart legs, each of said legs having a pin engaging surface thereon, said pawl legs being selectively pivotable into the orbital path of said pin so that only one of said pin engaging surfaces may engage said pin.

5. The invention as in claim 4 wherein said can opener includes a means for automatically shutting off said electric motor when the top of said can has been severed therefrom.

6. The invention as in claim 1 wherein said pin member and said pawl member cooperating toform a toggle linkage that interconnects said carrier member and said frame, said linkage having a fully extended condition corresponding to said can cutting position and a retracted or folded condition corresponding to said can receiving (or can removing) position, i

said means interconnecting said pushbutton and said pawl operative to selectively shift said pawl between the toggle extended and the toggle retracted positions, and

said pawl interconnecting means having a biasing means therein to assist in the shifting of said pawl when same is initiated by said pushbutton.

7. The invention as in claim 6 wherein said can opener includes a means for automatically shutting off said electric motor when the top of said can has been severed therefrom.

8. The invention as in claim 6 wherein said can opener includes a motor control means having a switch means which is operable responsive to the upward movement of said feed wheel to energize said motor prior to the piercing of the can end by said cutter element.

9. The invention as in claim 6 wherein said biasing means counterbalances said pawl to thereby assist in the pivoting of same, said biasing means including a spring attached to said pawl and operable to force said pawl to a rest position.

10. The invention as in claim 6 wherein said interconnecting means includes:

a plate pivoted to said frame, said plate being interconnected with said pushbutton and operable to pivot when said pushbutton is actuated,

a link member interconnecting said pawl and said plate,

means associated with said plate to move said link member in a direction corresponding to the movement of said plate thereby causing the pivotal movement of said pawl.

11. The invention as in claim 10 wherein said link moving means includes a means to limit the movement of said link when said pawl movement is temporarily preeluded.

12. The invention as in claim 2 wherein said pawl has pin engaging surface to thereby cushion the contracting respect to said pawl, and means for resiliently biasing said pin engaging surface to thereby cushion the contracting movement of same as said linkage is toggled toward its fully extended condition.

13. The invention as in claim 12 wherein said resiliently biasing means includes a compression spring located between said pin contacting surface and said pawl, said spring operable to cushion said surface as same moves inwardly against said pawl.

14. The invention as in claim 12 wherein said pawl has two spaced apart legs with pin engaging surfaces located therein, said apwl being selectively pivotable into the orbital path of said pin so that concurrent engagement of both surfaces is precluded.

15. The invention as in claim 14 wherein said spring loaded engaging surface is located on one of said spaced apart legs, said one of said legs being movable into the orbital path of said pin so that the toggling of said pin and said leg move said feed wheel into the can cutting position.

16. The invention as in claim 15 wherein said one of said legs is provided with a housing, a compression spring located interiorly of said housing, and a pin engaging extension reciprocally movable within said housing against said compression spring, said spring thereby cushioning the advance of said feed wheel as same moves the can for piercing of its end by the cutter element.

17. The invention as in claim 14 wherein said can opener includes a means for counterbalancing said pawl to assist in the pivoting of said pawl in accordance with the actuation of said pushbutton.

18. The invention as in claim 14 including means for automatically shutting off said electric motor when the top of said can has been severed therefrom.

References Cited UNITED STATES PATENTS 3,253,334 5/1966 McLean 304 2,789,345 4/1957 Klassen 304 HAROLD D. WHITEHEAD, Primary Examiner UNITED STATES PATENT OFFICE CERTIFICATE OF CORRECTION Patent No. 3 6l1,565 D t October 12. 1971 lnventofls) Robert E. McLean It is certified that error appears in the above-identified patent and that said Letters Patent are hereby corrected as shown below:

Col., 3 Line 50 "raiser" should be ---raised--.

Col. 5' Line 63 ".eelments" should be -el ements.

Col, 17 Line 3 0 "apwl" should be --pawl-.

Claim 12 should be corrected to read as follows:

--l2 The invention as in claim 2 wherein said pawl has a pin engaging. surface, said surface being movable with respe to said pawl, andmeans for resiliently biasing said pin engaging surface to there by cushion the contracting movement of same as said linkage is toggl ed toward its fully extended condition.--

Signed and sealed this 26th day of November 1974.

(SEAL) Attest:

McCOY M. GIBSON JR. C. MARSHALL DANN Attesting Officer Commissioner of Patents 

